WO2017080551A1 - Montage oscillant sans jeu au niveau d'un tendeur de découplage - Google Patents

Montage oscillant sans jeu au niveau d'un tendeur de découplage Download PDF

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Publication number
WO2017080551A1
WO2017080551A1 PCT/DE2016/200501 DE2016200501W WO2017080551A1 WO 2017080551 A1 WO2017080551 A1 WO 2017080551A1 DE 2016200501 W DE2016200501 W DE 2016200501W WO 2017080551 A1 WO2017080551 A1 WO 2017080551A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring element
clamping arm
base unit
pendulum
arm
Prior art date
Application number
PCT/DE2016/200501
Other languages
German (de)
English (en)
Inventor
Christian Hauck
Original Assignee
Schaeffler Technologies AG & Co. KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to ES16805275T priority Critical patent/ES2811333T3/es
Priority to US15/768,228 priority patent/US10788106B2/en
Priority to EP16805275.1A priority patent/EP3374666B1/fr
Priority to PL16805275T priority patent/PL3374666T3/pl
Priority to CN201680065577.8A priority patent/CN108350999B/zh
Priority to KR1020187013009A priority patent/KR20180079331A/ko
Publication of WO2017080551A1 publication Critical patent/WO2017080551A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1254—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
    • F16H7/1281—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
    • F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1209—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means
    • F16H7/1218—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means of the dry friction type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0874—Two or more finally actuated members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0893—Circular path

Definitions

  • the invention relates to a pendulum clamp for a continuous traction drive, preferably an endless belt drive of an internal combustion engine, such as a diesel or gasoline engine, a motor vehicle, such as a car, truck, bus, an agricultural utility vehicle or a motorcycle, a base unit and a separate, ring-shaped tensioner, wherein the tensioning arm is slidably mounted in a Gieitlagerungs- bereioh the base unit for allowing a rotational movement relative to the base unit
  • Such pendulum clamps which are also referred to as PendelroSienspanner or ring tensioner are already known from the prior art in various versions.
  • DE 1Q 2 ⁇ 11 084680 BS discloses a tensioning device for a belt drive, which has an endlessly circulating belt, an electric machine with a machine housing and a drive wheel and at least one further drive wheel, which is connected via the belt to the drive wheel in drive Connection stands.
  • the tensioning device itself comprises a tensioner housing, which is supported by a casting bearing about the axis of the drive wheel pivotable relative to the machine housing, two tensioning rollers which act on the belt in its U before and behind the drive wheel with biasing force, a spring force generating the biasing force , a tensioning arm movably mounted in the tensioner housing against the force of the spring element, one of the tensioning rollers being mounted on the tensioning arm and the other tensioning roller being fixedly mounted on the tensioning arm
  • Spanner housing is mounted, and a tensioner housing axially spanning bearing carrier.
  • the at least one spring element has a surface designed as a guide.
  • the spring element can be integrated in a particularly tight construction. If the casting surface is preferably supported / resting in the radial direction and / or in the axial direction on the casting support region or the clamping arm, the spring element can be used in a particularly targeted manner.
  • the at least one spring element may also have two sliding surfaces, each at one of two rear surfaces are arranged. As a result, a particularly low-wear training of Pederelemenies implemented.
  • the at least one spring element to apply a spring force in the radial direction (radial direction of the rotation axis of the tensioning arm) and / or in the axial direction (axial direction of the rotation axis of the tensioning arm) between the base unit and the span arm used particularly effectively
  • the at least one spring element is arranged in a radial gap and / or in an axial gap between the sliding bearing area and the clamping arm, it can be used in a versatile manner without great changes to the existing pendulum-type tensioner design.
  • a first spring element is arranged in a radial gap between the sliding bearing region and the clamping arm and a second Federeiement is arranged in an axial gap between the Gleitlagerungs Scheme and the clamping arm, thereby at least two spring elements are used in the pendulum clamp ⁇ the clamping arm Stably supported relative to the sliding bearing area in the respective direction.
  • a particularly effective reduction of the bearing clearance is implemented both in the radial and in the axial direction.
  • the at least one spring element is designed as a corrugated spring.
  • the at least one spring element is of annular or disc-shaped design, so that it can be inserted space-savingly into a radial or axial spa between the extension area and the tensioning arm.
  • the corrugated spring ring-shaped wherein the ' (inner and Au en ⁇ ) Dürchrriesser sic i circumferential direction wavy changed,
  • the wave spring disc-shaped it is advantageous if the axial side walls in wavy wavy wavy (ge bend). Thereby das... flower one spring element is made compact and inexpensive.
  • v is at least one spring element by means of a rotation lock connected to the Gleitiagerungs Symposium or the tensioning arm.
  • Spring element is configured specifically as Gleitfikiee, whereby the Hefsteil nation be further reduced.
  • Irisbesondere it is in this context advantageous if the at least one Federeiement by a formschiussige connection i direction of rotation of the clamping arm relative to the base unit ⁇ on the C feitiagerungs Scheme or the clamping arm against rotation set / held. Because then the rotation is easily made
  • the at least one spring element is supported on a sliding cover of the clamping arm. Because of this, the wear of the plain bearing area can be further reduced.
  • Fig. 1 is a perspective view of a pendulum tensioner according to the invention according to a preferred Ausus Entrysbeispiel.
  • the pendulum clamp is shown from one side, on which the clamping arm can be seen from the front
  • Fig. 2 ⁇ perspective view of the pendulum clamp shown partially cut in the longitudinal direction of FIG. 1, wherein the Gleitlagerstelie between a sliding bearing region of the base unit of the Pe deispa ners and to recognize the tensioning arm
  • 3 shows a detailed view of the area marked "III" in FIG. 2, which shows the spring elements used in an axial gap and a radial gap between the base unit and the tensioning arm
  • FIG. 4 shows a longitudinal section of the tensioning plunger according to the invention
  • FIG. 5 shows a detailed representation of the region marked "V" in FIG. 4, in which the two spring elements, as they are inserted between the casting storage area and the chip arm, are clearly recognizable, FIG.
  • FIG. 6 shows a perspective illustration of a part of the pende planner according to FIG.
  • FIG. 7 is a perspective view of a peripheral part of the pende planner according to FIG. 1, in: a storage area of the basal inside, the portion of the tensioning arm being illustrated, so that the two spring elements are particularly well recognizable in the form of corrugated springs;
  • Fig. 8 shows again a perspective representation of the scope of the Pendeispanner similar zü. ' , ⁇ : «toberde.r UmfengsbörSich now dargeielät in another angle, so that in particular the wavy extent of serving in an axial gap ' as an axial spring, second Detecting spring element is bar,
  • FIG. 9 again shows a perspective view of the pende planner according to FIG. 1, FIG.
  • Fig. 1 ö a perspective view of the first spring element, as shown in the
  • Fig. 1 1 is a perspective view of the second spring element, as it is used in the pendulum clamp of FIG.
  • FIG. 1 an inventive pendulum clamp 1 is illustrated according to a preferred embodiment.
  • the pendulum clamp 1 is designed as a pendulum belt tensioner and thus serves in operation For biasing a designed as a belt Endioszugrftittels a Endloszugstofftechnisches belt drive.
  • the Endioszug mean drive which is not shown here for clarity, connects in the operation of an internal combustion engine preferably a Popewelie / crankshaft of the internal combustion engine with another Drehteü, such as a drive shaft of an accessory, such as a generator.
  • the Rendelspanner 1 is designed as a ring tensioner and acting. Accordingly, the pendulum clamp 1 on an annular base unit 2, which is arranged in operation in the usual manner fixed to a generator housing.
  • the tensioning device 1 can be pushed onto the generator housing during operation.
  • the base unit. 2 has a receiving space 14, which surrounds at least one bow springs 15 running in the middle of their circumference (with respect to an axis of rotation 26 of the tightening arm 3) of the tightening clip 1.
  • the Bogenfedem 15 are supported / inserted in the circumferential direction between a portion of the base unit 2 and a portion of relative to the base unit 2 about the rotation axis 26 rotatably mounted clamping arm 3.
  • a tensioning roller 17 is rotatably / rotatably mounted, soft tensioning roller 17 in operation with the EndloszugmitteS in the form of the belt in contact and is pressed due to the spring force of the Bogenfedem 15 by means of a biasing force to the Endloszugfflettei ,
  • a sliding bearing 27 / a slide bearing is provided on the pendulum clamp 1 for supporting the clamping arm 3 relative to the base unit 2.
  • the sliding bearing portion 4 forms together with a radially outer / rad ial externa ßeren flange portion 18 of the clamping arm 3, the sliding bearing 27 from.
  • the fanning area 18 has a sliding lining 13, preferably made of plastic, wherein the sliding layer can be seen particularly well in FIGS. 3 and 5.
  • the pouring area 4 is essentially formed by a storage space 28 of the base unit 2 which transits in the shape of a channel.
  • the plain bearing area 4 of the base unit 2 is connected to the receiving space 14.
  • a first support portion 19 of the target storage portion 4 extending radially inward adjacent to a first axial side of the clamp arm 3 and a second support portion 20 in the form of a lid 21 adjacent to a second axial side opposite the first side of the clamping arm 3 extends radially inward, form the storage space 28 together.
  • the lid 21 is again detachably attached to the first support portion 19.
  • the flange portion 18 is arranged together with the sliding coating 13. From radially outside the clamping arm 3 is also also surrounded by the first ⁇ bstütz Scheme 19.
  • the base unit 2 forms a substantially channel-shaped U-shaped Gieitlagerungs- area 4 viewed in Quersch itit, which is open radially inward and forms the storage space 28 for the flange 18, which at its radially outer region with the sliding coating thirteenth protrudes into it.
  • FIGS. 4 and 5 in the radial direction between a radial outer side 2 of the sliding lining 13 / of the chip arm; 3 and the first ⁇ bstütz Scheme 19 / the Gieitlagerungs Club 4 a Radialspait 9 is formed.
  • This first spring element 5 is also particularly well in its entirety in conjunction with FIGS. 6 to 9 and in sole consideration in FIG. 10 easy to recognize.
  • the first spring element 5 is annular (FIG. 10) and extends along the circumference / circumferential direction of the pendulum tensioner 1 in a wave form.
  • the first spring element 5 is thus formed as a whale leather.
  • An inner diameter and an outer diameter (due to the same thickness of the sheet metal thickness) of the first spring element 5 change wavy (expanded and reduced again) in the circumferential dimension of the pendulum clamp 1 considered.
  • the sliding bearing 27 is spring-biased, ie spring-biased in radial direction.
  • the first spring element 5 is thus inserted / clamped in the radial gap 9 in any operating state of radial prestressing, d, h, applying a radial prestressing / radialia force ,
  • a radial clearance is between the clamping arm 3 and the base unit 2 is fixed.
  • the clamping arm 3 is always aligned relative to the base unit 2 in the radial direction.
  • the first spring element 6 also has an anti-rotation 11 au !.
  • Anti-rotation is implemented by a running in Radsalraum bulge 23.
  • the bulge 23 is positively inserted into a recess (FIG. 9) formed in a complementary manner to the recess 24 in the lubricant storage region 4, namely in the first support region 19.
  • a form-fitting connection 1 is realized, by means of which the first spring element 5 is held against rotation relative to the base unit 2 / supported.
  • the first ring-shaped spring element 5 With its outer peripheral side, the first ring-shaped spring element 5 thus engages in a rotationally fixed manner on an inner circumferential side of the first supporting region 19 during operation.
  • the first Federeiement 5 as a Gieit Structure, hereinafter referred to as first Gieit Structure 7, designed.
  • the first sliding surface 7 forms a materially and geometrically optimized surface of the first spring element 5 with regard to the sliding mounting of the tensioning arm 2 / sliding lining 13.
  • the saving arm 3 is slidably movable along this first sliding surface 7 (by rotation).
  • ei axial gap 10 formed in this Axlais journallt 10 aestereiement, namely a second Federeiement 6 used.
  • the embodiment of the second spring element 6 can be seen again in FIGS. 7 and 8 and separately in FIG. 11.
  • the second spring element 8 is disc-shaped with a central through-hull / riftgusionnförmig equipped.
  • the second Federefe- erent 6 is like the first Federeiement 5 configured as a wicker.
  • the second spring element ⁇ is formed in such a way that its axial side walls 25a, 25b extend in an undulating direction in the circumferential direction.
  • the second spring element 6 is made from a metal spring plate and, viewed along the circumference, remains constant in its plate thickness / thickness, both a first side wall 25a oriented in the first axial side and a first side wall 25a.
  • ne second side wall 25b aligned with the second axial side are respectively designed as first and second sliding surfaces 7, 8. It is also possible in turn to arrange the second spring element 6 against rotation on the base unit 2 (or the clamping bar 3). In this case, then again only one, preferably the
  • the second Federeiement 6 is under axial bias, ie unier application of Axialyorpressive / Axialfederkraft, inserted / clamped in the Axlalspait 10.
  • the second spring element 8 brings such a spring force on the Gteitlagerungsbe- area 4 and on the clamping arm 3, that the clamping arm 3 is received without play in the axial direction relative to the Gteitiagerungs Scheme 4.
  • a backlash-free reception of the tensioning arm 3 implemented in both the axial direction and in the radial direction is realized.
  • a radial clearance is achieved.
  • first spring element 5 ⁇ is used, which is under a certain Vbrspanniing.Thus, it is ensured that the tensioner 1 in the bearing 27 radially
  • an axial corrugated spring ⁇ second spring element 6 is used, which eliminates play in the axial direction.
  • This spring 8 is also slightly preloaded. The spring stiffnesses are designed so that their natural frequencies are above the Radiofretf Uenzen the pendulum spreader 1 and lie to it no Aufscriwingvorgang more comes.
  • the springs 5, 6 offer the advantage of being able to set the pendulum damping in a targeted manner, depending on the selected preload.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

L'invention concerne un tendeur oscillant (1) pour un mécanisme de traction sans fin d'un moteur à combustion interne, comportant une unité de base (2) et un bras de tension (3) annulaire séparé de cette dernière, le bras de tension (3) étant monté de manière à coulisser dans une zone de montage coulissant (4) de l'unité de base (2) pour permettre un mouvement de rotation par rapport à l'unité de base (2). Entre la zone de montage coulissant (4) de l'unité de base (2) et le bras de tension (3) est inséré au moins un élément ressort (5, 6) serrant l'unité de base (2) et le bras de tension (3) l'un contre l'autre.
PCT/DE2016/200501 2015-11-11 2016-11-08 Montage oscillant sans jeu au niveau d'un tendeur de découplage WO2017080551A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
ES16805275T ES2811333T3 (es) 2015-11-11 2016-11-08 Soporte de péndulo sin holgura en el tensor de desacoplamiento
US15/768,228 US10788106B2 (en) 2015-11-11 2016-11-08 Clearance-free self-aligning bearing on the decoupling tensioner
EP16805275.1A EP3374666B1 (fr) 2015-11-11 2016-11-08 Montage oscillant sans jeu au niveau d'un tendeur de découplage
PL16805275T PL3374666T3 (pl) 2015-11-11 2016-11-08 Bezluzowe ułożyskowanie wahadłowe na napinaczu odsprzęgającym
CN201680065577.8A CN108350999B (zh) 2015-11-11 2016-11-08 在脱耦张紧器上的无间隙的摆动支承装置
KR1020187013009A KR20180079331A (ko) 2015-11-11 2016-11-08 디커플링 텐셔너 상의 틈새 없는 자동 조심 베어링

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015222203.9 2015-11-11
DE102015222203.9A DE102015222203B4 (de) 2015-11-11 2015-11-11 Spielfreie Pendellagerung am Entkopplungsspanner

Publications (1)

Publication Number Publication Date
WO2017080551A1 true WO2017080551A1 (fr) 2017-05-18

Family

ID=57471634

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2016/200501 WO2017080551A1 (fr) 2015-11-11 2016-11-08 Montage oscillant sans jeu au niveau d'un tendeur de découplage

Country Status (8)

Country Link
US (1) US10788106B2 (fr)
EP (1) EP3374666B1 (fr)
KR (1) KR20180079331A (fr)
CN (1) CN108350999B (fr)
DE (1) DE102015222203B4 (fr)
ES (1) ES2811333T3 (fr)
PL (1) PL3374666T3 (fr)
WO (1) WO2017080551A1 (fr)

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AU2019236060B2 (en) * 2018-03-13 2021-12-16 Gates Corporation Orbital tensioner

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WO2014100894A1 (fr) 2012-12-26 2014-07-03 Litens Automotive Partnership Ensemble tendeur orbital
EP3161346B1 (fr) * 2014-06-26 2020-06-24 Litens Automotive Partnership Ensemble tendeur orbital
DE102016217933B4 (de) * 2016-09-20 2020-06-04 Schaeffler Technologies AG & Co. KG Riemenspanner
IT201700053588A1 (it) * 2017-05-17 2018-11-17 Dayco Europe Srl Tenditore per una trasmissione accessori di un autoveicolo
DE102017116000A1 (de) 2017-07-17 2019-01-17 Muhr Und Bender Kg Riemenspannvorrichtung
KR102506926B1 (ko) * 2017-12-18 2023-03-07 현대자동차 주식회사 듀얼 텐셔너 및 이를 적용한 엔진
CN109838520B (zh) * 2018-11-12 2020-06-30 宁波丰茂远东橡胶有限公司 一种双液压自动张紧器
CN109340507A (zh) * 2018-12-10 2019-02-15 广西玉柴机器股份有限公司 一种振动减小的飞轮壳
US11255414B2 (en) * 2019-05-15 2022-02-22 Gates Corporation Tensioner

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DE102011084680B3 (de) 2011-10-18 2012-11-22 Schaeffler Technologies AG & Co. KG Spannvorrichtung für einen Riementrieb und Elektromaschine mit einer derartigen Spannvorrichtung
DE102012209028A1 (de) 2012-05-30 2013-12-05 Schaeffler Technologies AG & Co. KG Spannvorrichtung für einen Riementrieb und Elektromaschine mit einer derartigen Spannvorrichtung
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DE102015222203A1 (de) 2017-05-11
EP3374666B1 (fr) 2020-06-24
DE102015222203B4 (de) 2020-03-12
CN108350999B (zh) 2021-08-24
CN108350999A (zh) 2018-07-31
US20180320765A1 (en) 2018-11-08
KR20180079331A (ko) 2018-07-10
EP3374666A1 (fr) 2018-09-19
US10788106B2 (en) 2020-09-29
PL3374666T3 (pl) 2020-11-16

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